【摘要】：齒輪轉(zhuǎn)子系統(tǒng)是旋轉(zhuǎn)機(jī)械的主要傳動(dòng)系統(tǒng),是各種設(shè)備中應(yīng)用最廣的動(dòng)力傳遞裝置。由于制造、安裝誤差和輪齒變形等因素,齒輪在嚙合過程中難免產(chǎn)生振動(dòng)和沖擊,齒廓修形是優(yōu)化接觸、彌補(bǔ)誤差、降低振動(dòng)和沖擊的有效手段。本文基于ANSYS軟件建立考慮齒頂修緣的準(zhǔn)靜態(tài)直齒輪副嚙合有限元模型,輸出時(shí)變嚙合剛度和靜態(tài)傳遞誤差。在此基礎(chǔ)上,基于MATLAB軟件建立直齒輪副嚙合動(dòng)力學(xué)模型,與轉(zhuǎn)子有限元模型耦合形成直齒輪-轉(zhuǎn)子系統(tǒng)彎扭軸擺全自由度有限元模型。考慮時(shí)變嚙合剛度、靜態(tài)傳遞誤差、扭轉(zhuǎn)激勵(lì)以及齒側(cè)間隙,對(duì)直齒輪-轉(zhuǎn)子系統(tǒng)進(jìn)行模態(tài)分析以及動(dòng)力學(xué)特性分析。主要內(nèi)容如下： (1)基于ANSYS軟件,在準(zhǔn)靜態(tài)下建立直齒輪副嚙合有限元模型,對(duì)其進(jìn)行靜力學(xué)分析,在僅考慮輪齒變形的前提下,計(jì)算不同扭矩作用下考慮齒頂修緣的齒輪的時(shí)變嚙合剛度和靜態(tài)傳遞誤差,為直齒輪-轉(zhuǎn)子系統(tǒng)動(dòng)力學(xué)特性分析提供數(shù)據(jù)支持。通過分析得出不同加載扭矩將引起嚙合剛度和靜態(tài)傳遞誤差整體幅值的變化,而齒頂修緣能夠緩和單雙齒交替區(qū)的突變,使嚙合頻率的高頻成分幅值發(fā)生變化。 (2)建立直齒輪副嚙合動(dòng)力學(xué)模型,與轉(zhuǎn)子有限元模型耦合形成直齒輪-轉(zhuǎn)子有限元模型。假定嚙合剛度為定值,對(duì)靜態(tài)傳遞誤差作用下的系統(tǒng)響應(yīng)進(jìn)行求解得出靜態(tài)傳遞誤差的基頻、高頻成分分別激起幅頻響應(yīng)的有關(guān)彎扭耦合的主共振峰和超諧波共振峰。考慮時(shí)變嚙合剛度的影響,對(duì)系統(tǒng)施加定值扭轉(zhuǎn)激勵(lì),分析表明時(shí)變嚙合剛度的基頻成分也將使系統(tǒng)產(chǎn)生基頻以及倍頻成分。另外由于時(shí)變嚙合剛度和正弦扭轉(zhuǎn)激勵(lì)相互影響,系統(tǒng)將產(chǎn)生嚙合頻率及其倍頻、轉(zhuǎn)頻以及嚙合頻率與轉(zhuǎn)頻的和頻、差頻等復(fù)雜的頻率成分。 (3)考慮齒頂修緣條件下的時(shí)變嚙合剛度和靜態(tài)傳遞誤差,分析不同扭矩下不同修緣量對(duì)系統(tǒng)振動(dòng)響應(yīng)的影響。齒頂修緣能夠降低除共振峰處的動(dòng)力學(xué)響應(yīng)幅值,抑制加速度幅值波動(dòng),減少振動(dòng)和沖擊,并且不同扭矩對(duì)應(yīng)的最優(yōu)修緣量不同,隨著齒頂修緣量的增加振動(dòng)響應(yīng)幅值并不是持續(xù)降低。 (4)考慮齒側(cè)間隙,建立僅考慮扭轉(zhuǎn)自由度的動(dòng)力學(xué)模型,分析不同系統(tǒng)參數(shù)下齒側(cè)間隙對(duì)系統(tǒng)動(dòng)力學(xué)特性的影響。隨著齒側(cè)間隙的增大,系統(tǒng)硬式非線性特性以及雙邊沖擊狀態(tài)逐漸消失,均呈現(xiàn)為“軟化曲線”。隨著阻尼的增大系統(tǒng)幅頻響應(yīng)幅值逐漸減少,硬式非線性特性和共振峰處的跳躍現(xiàn)象逐漸消失。隨著扭轉(zhuǎn)激勵(lì)的增大系統(tǒng)幅頻響應(yīng)幅值逐漸增大,硬式非線性特性逐漸顯著。由于齒側(cè)間隙對(duì)振動(dòng)響應(yīng)的影響依賴于系統(tǒng)參數(shù),對(duì)于本文所研究的齒輪-轉(zhuǎn)子系統(tǒng),考慮齒側(cè)間隙情況下系統(tǒng)的幅頻響應(yīng)未出現(xiàn)跳躍現(xiàn)象。 本文通過數(shù)值仿真方法,主要對(duì)考慮齒頂修緣的直齒輪-轉(zhuǎn)子系統(tǒng)進(jìn)行動(dòng)力學(xué)特性研究,研究結(jié)果可為直齒輪-轉(zhuǎn)子系統(tǒng)的動(dòng)態(tài)響應(yīng)計(jì)算以及結(jié)構(gòu)設(shè)計(jì)提供理論依據(jù)。
[Abstract]:Gear rotor system is the main transmission system of rotating machinery. It is the most widely used power transmission device in all kinds of equipment. Because of the factors such as manufacturing, installation error and gear tooth deformation, the gear is unavoidable to produce vibration and impact during the meshing process. The tooth profile modification is an effective means to optimize contact, make up error, reduce vibration and impact. The ANSYS software establishes the finite element model of the quasi static spur gear pair, which considers the tooth top repair edge, and the time-varying meshing stiffness and the static transmission error. On this basis, based on the MATLAB software, the meshing dynamic model of the spur gear is established and coupled with the rotor finite element model to form the full degree of freedom finite element model of the bending and torsion axis swing of the spur rotor system. Considering the time-varying meshing stiffness, static transmission error, torsional excitation and tooth side gap, the modal analysis and dynamic characteristic analysis of the spur gear rotor system are carried out. The main contents are as follows:
(1) based on the ANSYS software, the finite element model of the spur gear meshing is established under the quasi static state, and the statics analysis is carried out. The time-varying meshing stiffness and the static transmission error of the gear with the tooth top repair edge are calculated under the condition of only the tooth deformation, which provides the data support for the dynamic characteristics analysis of the spur gear rotor system. The analysis shows that the different loading torque will cause the change of the overall amplitude of the meshing stiffness and the static transmission error, and the tooth top repair edge can ease the mutation of the single and double teeth alternation zone, and make the high-frequency component amplitude of the meshing frequency change.
(2) establish the meshing dynamic model of the spur gear, coupled with the rotor finite element model to form the finite element model of the spur gear rotor. Assuming the meshing stiffness as the fixed value, the system response of the static transmission error is solved to get the basic frequency of the static transmission error and the main resonance of the amplitude frequency response of the high frequency component to the amplitude frequency response. Considering the influence of time-varying meshing stiffness, considering the influence of time-varying meshing stiffness, the fixed value torsion excitation is applied to the system. The analysis shows that the basic frequency component of the time-varying meshing stiffness will also make the system produce fundamental frequency and frequency doubling component. And complex frequency components such as frequency and frequency, frequency difference.
(3) considering the time varying meshing stiffness and the static transmission error under the tooth top repair edge, the influence of the different trimming amount on the vibration response of the system under different torque can be analyzed. The tooth top repair edge can reduce the amplitude of the dynamic response except the resonance peak, restrain the fluctuation of the acceleration amplitude, reduce the vibration and impact, and the optimal trimming amount corresponding to the different torque is not. The amplitude of vibration response does not decrease continuously with the increase of tooth margin.
(4) considering the tooth side gap, a dynamic model which only considers the torsional degree of freedom is established, and the influence of the tooth side gap on the dynamic characteristics of the system is analyzed under the different system parameters. With the increase of the tooth side gap, the hard nonlinear characteristics and the bilateral impact state gradually disappear, all of which are now "softening curves". With the damping increasing the system amplitude The amplitude of the frequency response is gradually reduced, the hard nonlinear characteristics and the jumping phenomenon at the resonance peak gradually disappear. With the increase of the torsional excitation, the amplitude of the amplitude frequency response of the system increases gradually, and the hard type nonlinear characteristic is gradually obvious. There is no jumping phenomenon when the amplitude frequency response of the system is taken into account.
In this paper, the numerical simulation method is used to study the dynamic characteristics of the spur rotor system, which considers the tooth top repair edge. The results can provide the theoretical basis for the dynamic response calculation and the structure design of the spur gear rotor system.
【學(xué)位授予單位】：東北大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2013
【分類號(hào)】：TH132.41

【參考文獻(xiàn)】

相關(guān)期刊論文 前10條

1 宋雪萍,于濤,李國平,聞邦椿;齒輪軸系彎扭耦合振動(dòng)特性[J];東北大學(xué)學(xué)報(bào);2005年10期

2 張希康;;漸開線齒輪齒頂修緣的計(jì)算與加工[J];齒輪;1985年06期

3 夏伯乾;宋現(xiàn)洲;;DH型透平壓縮機(jī)齒輪耦合轉(zhuǎn)子—滑動(dòng)軸承系統(tǒng)動(dòng)力學(xué)設(shè)計(jì)的理論與應(yīng)用[J];機(jī)械傳動(dòng);2010年07期

4 張鎖懷,石守紅,丘大謀;齒輪耦合的轉(zhuǎn)子-軸承系統(tǒng)的非線性模型[J];機(jī)械科學(xué)與技術(shù);2001年02期

5 韓玉強(qiáng),石守紅,張鎖懷;齒輪耦合對(duì)轉(zhuǎn)子-軸承系統(tǒng)固有特性的影響[J];機(jī)械科學(xué)與技術(shù);2003年01期

6 宋雪萍;劉樹英;聞邦椿;;齒輪-轉(zhuǎn)子系統(tǒng)的振動(dòng)特性分析[J];機(jī)械科學(xué)與技術(shù);2006年02期

7 李潤方,韓西,林騰蛟,鐘厲;齒輪系統(tǒng)耦合振動(dòng)的理論分析與試驗(yàn)研究[J];機(jī)械工程學(xué)報(bào);2000年06期

8 張鎖懷,李憶平,丘大謀;齒輪耦合的轉(zhuǎn)子-軸承系統(tǒng)非線性動(dòng)力特性的研究[J];機(jī)械工程學(xué)報(bào);2001年09期

9 張鎖懷,沈允文,丘大謀;齒輪耦合的轉(zhuǎn)子軸承系統(tǒng)的不平衡響應(yīng)[J];機(jī)械工程學(xué)報(bào);2002年06期

10 王三民,沈允文,董海軍;含間隙和時(shí)變嚙合剛度的弧齒錐齒輪傳動(dòng)系統(tǒng)非線性振動(dòng)特性研究[J];機(jī)械工程學(xué)報(bào);2003年02期

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